KR20140098457A - Electric motor-driven compressor - Google Patents
Electric motor-driven compressor Download PDFInfo
- Publication number
- KR20140098457A KR20140098457A KR1020130011123A KR20130011123A KR20140098457A KR 20140098457 A KR20140098457 A KR 20140098457A KR 1020130011123 A KR1020130011123 A KR 1020130011123A KR 20130011123 A KR20130011123 A KR 20130011123A KR 20140098457 A KR20140098457 A KR 20140098457A
- Authority
- KR
- South Korea
- Prior art keywords
- main bearing
- damping member
- housing
- circumferential surface
- bearing
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric compressor, and more particularly, to a coupling structure between a compressor housing unit and an inverter assembly constituting an electric compressor.
Generally, a compressor used in an air conditioning system of an automobile performs a function of sucking refrigerant that has been evaporated from an evaporator and converting it into a high-temperature and high-pressure state which is easy to be liquefied and delivering it to a condenser.
The compressor is provided with a driving force from an engine of a vehicle to perform a compression operation, and a method of performing a compression operation by driving an electric motor according to a separate power supply.
In the case of an electric compressor that performs a compressing operation by driving an electric motor, the power of the
The
An
A main bearing 40 is provided around the front end of the
2, the
However, due to the difference in thermal expansion coefficient between the material of the
That is, when the tolerance of the main bearing 40 is selected on the basis of a low temperature, there is a problem that the internal tolerance of the main bearing 40 is increased at a high temperature and noise is generated. In consideration of this, There has been a problem of causing the main bearing 40 to be disengaged.
In addition, in the case of the
SUMMARY OF THE INVENTION It is an object of the present invention to improve a coupling structure between a bearing and a housing part to thereby improve noise or noise due to operation failure of the bearing, And to provide an electric compressor according to a new type in which the coupling can be smoothly performed.
According to an aspect of the present invention, there is provided a variable displacement swash plate type compressor, including a motor unit and a compression mechanism unit, the main bearing supporting a drive shaft coupled to a rotor of the motor unit, The main bearing is damped so as to be fixed in the housing part regardless of the temperature change while compensating for the engagement tolerance of the main bearing, between the engagement part of the main bearing and the housing part, And a damping member for supporting and supporting the force.
Here, an accommodating groove for accommodating the damping member is formed on one of the inner circumferential surface of the housing portion facing the outer circumferential surface of the main bearing or the outer circumferential surface of the main bearing, so that the undesired axial movement In order to prevent the problem.
The damping member may include a ring-shaped ring-shaped body surrounding the outer circumferential surface of the main bearing, and elastic protrusions protruding from the outer circumferential surface of the ring-shaped body.
In addition, the elastic protrusions constituting the damping member are provided in a plurality of along the circumferential direction of the ring-shaped body, and are spaced apart from each other with a predetermined distance therebetween.
In addition, each of the elastic protrusions constituting the damping member is formed so as to protrude toward at least one of the outer circumferential surface of the main bearing and the inner circumferential surface of the housing portion, and the spacing distance and the protrusion height between the elastic protrusions And is designed differently depending on the pressing force of the bearing.
Further, the ring-shaped body constituting the damping member is formed by cutting at one end.
In the electric compressor according to the present invention as described above, even if the shape of the coupling portion between the main bearing and the housing portion caused by the temperature change in the housing portion is generated, due to the damping force provided from the damping member, The coupling force between the main bearing and the main bearing can be always kept constant, thereby preventing the occurrence of start-up noise and the disconnection of the main bearing.
Particularly, since the main bearing can be always kept in a stable press-fit state in the housing part, the vertical vibration of the drive shaft due to the swinging of the main bearing can also be prevented originally, Or damage to the compression mechanism, etc.) can be prevented.
1 is a cross-sectional view illustrating an internal structure of a conventional electric compressor
Fig. 2 is an enlarged view of the " A &
3 is a cross-sectional view illustrating an internal structure of an electric compressor according to a preferred embodiment of the present invention
Fig. 4 is an enlarged view of " B &
5 is a perspective view illustrating a damping member of an electric compressor according to a preferred embodiment of the present invention.
Hereinafter, a preferred embodiment of the electric compressor of the present invention will be described in more detail with reference to FIGS. 3 to 5.
Fig. 4 is an enlarged view of the portion " B " in Fig. 2, and Fig. 5 is an enlarged view of the electric compressor according to the embodiment of the present invention. Fig. 3 is a perspective view showing the damping member of Fig.
As can be seen from these drawings, the electric compressor according to the embodiment of the present invention mainly includes a
This will be described in more detail below for each configuration.
First, the
The
At the rear of the
Of course, although not shown, the
Next, the
The
Here, the stator 210 has a plurality of ring-shaped core pieces passing through the center thereof, and is formed into a cylindrical shape. A coil (not shown) is wound around the stator 210.
The
An
Next, the
The
The
The
The damping
That is, the coupling allowance of the
In the embodiment of the present invention, the
5, the
At this time, since the ring-
When the
The
In particular, each of the
4, a receiving
Of course, the receiving
The damping
Hereinafter, the operation state of the electric compressor according to the embodiment of the present invention and the action of the damping
First, when power is externally applied to the motor-driven compressor, electric power is supplied from the
When the
When the above process is performed, the refrigerant flows into the
Meanwhile, during the compression operation of the electric compressor described above, a temperature change occurs in the
A damping
As a result, the electric compressor according to the embodiment of the present invention is capable of preventing the start noise or the seizing of the
Meanwhile, the damping
Although not shown, the damping
As described above, the damping
100.
111.
120.
140.
210.
300.
320. Turning
410.
412.
414. Receiving
430.
510. Ring-shaped
600. Drive
Claims (6)
The main bearing 410 is fixed within the housing part 100 regardless of the temperature change while compensating for the engagement tolerance of the main bearing 410 between the coupling part between the main bearing 410 and the housing part 100. [ Further comprising a damping member (500) for supporting and supporting the damping force so as to form the damping force.
The inner circumferential surface of the housing part 100 facing the outer circumferential surface of the main bearing 410 or the outer circumferential surface of the main bearing 410 is provided with a receiving groove 414 for receiving the damping member 500 Is configured to prevent undesired axial movement of the damping member (500).
The damping member (500)
A ring-shaped ring-shaped body 510 surrounding the outer circumferential surface of the bearing 410,
And an elastic protrusion (520) protruding from an outer circumferential surface of the ring-shaped body (510).
Wherein the elastic protrusions (520) of the damping member (500) are provided in a plurality of along the circumferential direction of the ring-shaped body (510) and spaced apart from each other with a predetermined distance therebetween.
The elastic protrusions 520 of the damping member 500 are formed to protrude toward at least one of the outer circumferential surface of the main bearing 410 and the inner circumferential surface of the housing portion 100,
Wherein the spacing distance and the protrusion height between the elastic protrusions (520) are designed differently according to the pressing force of the main bearing (410) according to the temperature change.
Wherein the ring-shaped body (510) constituting the damping member (500) is formed by cutting one end of the ring-shaped body (510).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020130011123A KR20140098457A (en) | 2013-01-31 | 2013-01-31 | Electric motor-driven compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020130011123A KR20140098457A (en) | 2013-01-31 | 2013-01-31 | Electric motor-driven compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
KR20140098457A true KR20140098457A (en) | 2014-08-08 |
Family
ID=51745248
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
KR1020130011123A KR20140098457A (en) | 2013-01-31 | 2013-01-31 | Electric motor-driven compressor |
Country Status (1)
Country | Link |
---|---|
KR (1) | KR20140098457A (en) |
-
2013
- 2013-01-31 KR KR1020130011123A patent/KR20140098457A/en not_active Application Discontinuation
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
E902 | Notification of reason for refusal | ||
E601 | Decision to refuse application |